Mobile compacting apparatus

ABSTRACT

A mobile compacting apparatus comprising a vehicle chassis with a feeding conveyor at the forward end and an elevating conveyor co-operating therewith. A plural stage compacting device cooperates with the elevating conveyor to receive material therefrom and compact the material to great density. An easily accessible hopper may be detachably secured about the feeding conveyor. An operator&#39;&#39;s station is disposed at the forward end of the chassis directly above the elevating conveyor. A foldable unloader conveyor is disposed at the rearward end of the chassis. Control means are provided for co-ordinating the cycling of the compacting device with the operation of the unloader. A moveable, curved closure plate in the compacting device permits a continuous reception of material into the charging chamber of the device with minimal resistance to movement of the plate. The operating cycle of the compacting device may be shifted to provide the most efficient and effective handling of different materials.

D United States Patent l 1 1 m1 3,908,540

Broman 1 Sept. 30, 1975 MOBILE COMPACTING APPARATUS s7 ABSTRACT lnvcnmr: Harold Bmmans Kcnmorc- A mobile compacting apparatus comprising a vehicle Assign: Sm) pac Corporation, Tonuwundm chassis with a feeding conveyor at the forward end and an elevating conveyor co-operating therewith. A plural stage compacting device cooperates with the 22 FlCd: 1972 elevating conveyor to receive material therefrom and AppL N; 299587 compact the material to great density. An easily accessible hopper may be detachably secured about the feeding conveyor. An operators station is disposed at CL 100/2153 37/10; 100/190; the forward end of the chassis directly above the ele- 100/218; 100/26 R vating conveyor. A foldable unloader conveyor is dislnt. B30b 15/30 posed at the rearward end f the Chassis; Comm] held of means are provided for co-ordinating the cycling of the compacting device with the operation of the unloader. A moveable. curved closure plate in the com- References cued pacting device permits a continuous reception of ma- UNITED STATES PATENTS terial into the charging chamber of the device with lul ill /26 Livengood a L d O 0 w Primary E.\'uniinerBilly J. Wilhitc Attorney. Agent. or FirmBacon and Thomas US. Patent Sept. 30,1975 Sheet 1 Of6 3,908,540

S. Patent Sept. 30,1975

Sheet 3 of 6 MOBILE COMPACTING APPARATUS BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a mobile compacting apparatus capable of compressing various types of loose materials, particularly solid waste and snow, into blocks or bales to vastly reduce the time and effort required for the removal and disposal of such materials.

Vehicular units for collecting and packing refuse are well known in the art. Such units usually include large storage compartments into which refuse is repeatedly compressed. While these units are capable of reducing the volume of refuse by about six times, a problem exists in that the units still must leave the collection area at frequent intervals. Also, since unloading of the vehicular units causes the refuse to return to the loose condition, the units have little or no effectiveness in alleviating the overall problems of said waste disposal.

The use of mobile compacting units has also been proposed for the removal of snow. The conventional snow plow or snow blower which directs snow to the side of a street is unsatisfactory for use in urban areas since large quantities of snow are piled adjacent to streets and sidewalks thereby obstructing the movement of vehicular traffic and pedestrians. The use by municipalities of mechanical equipment for loading snow into waiting trucks creates problems of its own. While the trucks can be loaded in a matter of minutes, they must usually travel substantial distances to a dumping site. Such an operation is highly inefficient and creates a problem in that dumping sites large enough to handle the huge volume of snow collected in this way often cannot be found within a reasonable distance from the snow removal area.

Mobile snow compacting machines have heretofore been proposed to help alleviate and reduce the above mentioned problems. However, none of the prior art devices provide an apparatus suitable for use on city streets with their accompanying curbs and other obstructions. Further, none of the prior art devices provide for a device to efficiently and effectively compact snow, and none provide satisfactory means for disposing of compressed quantities of snow.

The invention also relates to a compacting apparatus capable of handling a variety of materials such as refuse, snow and ice and having different operating cycles for each material with a means for readily shifting from one cycle to another. Such a device has not heretofore been known.

Another aspect of the invention relates to a moveable cover plate for the charging chamber of the compacting apparatus itself. While moveable cover plates have heretofore been proposed for changing chambers of presses, none of the known devices provide for a cover plate which will encounter only minimal resistance to movement and which will permit asubstantially continuous reception of material into the apparatus regardless of the position of the moveable compression member in the chamber.

2. Description of the Prior Art U.S. Pat. No. 3,583,164, to CA. Sherrill, discloses a mobile refuse handling system utilizing a baling press for receiving and compressing refuse. Here, refuse must be supplied to a hopper located above the press. The present invention improves upon this arrangement by providing for the disposition of the hopper at ground level. Also, in the device of the present invention there is no need for separate human operators for the baling press, the bale handling apparatus, and the towing vehicle.

U.S. Pat. No. 1,523,012, to F. Gettelman; U.S. Pat. No. 1,561,472 to B.A. Linderman; U.S. Pat. No. 1,708,376, to DB. Cook and U.S. Pat. No. 3,149,428, to ME. Hukill all disclose mobile snow compacting devices wherein. The operators station is located either to one side of the vehicle or at a position remote from the forward end of the vehicle where snow is received. The device of the present invention represents an advance over these prior art devices by significantly improving visibility. This is important since, on city streets, the presence of curbs and other obstructions makes it essential that the operator have a clear view of the entire roadway lying in the path of the snow receiving apparatus. Also, the device of the present invention is so constructed that the snow conveying means does not extend above the operator station to obstruct the operators visibility.

U.S. Pat. No. 2,244,078, to BB. Perlberg discloses a plural stage baling press having a moveable cover for the first stage. The cover is a heavy casting with linkage elements for moving the same mounted at the upper exterior surface. Although such an arrangement is well suited to the purpose for which it is intended, it would be unsuitable for continuous reception of loose material. This is so because a substantial quantity of loose material would build up above the cover when the cover is closed. In the device of the present invention, problems associated with this build up are minimized through use ofa special, curved closure plate and associated apparatus at the mouth of the charging chamber of the compacting device.

OBJECTS OF THE INVENTION It is an object of the present invention to provide a mobile compacting apparatus capable of compressing various materials into dense blocks or bales, which apparatus is readily convertible to different operating modes for compressing different materials.

It is a more particular object of the invention to provide a mobile compacting apparatus having a refuse handling mode of operation, a snow handling mode of operation, and an ice handling mode of operation, which apparatus is readily convertible from one mode to the other.

It is a further object of the invention to provide a mobile compacting app'aratus having a feeding conveyor disposed at the street or ground level, and an elevating conveyor co-operating therewith for charging a compacting apparatus.

It is also an object of the invention to provide a hopper partially enclosing the feeding conveyor to facilitate the delivery of material to the apparatus.

It is another object of the invention to provide a detachable hopper means about the feeding conveyor whereby the hopper may be used for one mode of operation but removed for another mode.

It is also an object of the invention to provide an operators station at the forward end of the vehicle, which station is laterally centered on the vehicle above the elevating conveyor to provide clear visibility of the entire roadway ahead of the feeding conveyor.

Another object of the invention is the provision of an automatic unloading device on the mobile compacting apparatus for automatically transporting blocks or bales of compressed material from the discharge opening of the compacting device to a truck following behind the mobile unit.

It is a further object of the invention to provide such an unloading device which is retractable when not in use.

It is also an object of the invention to provide a mobile compacting device with an unloader and a means to effect cooperation between the operating cycle of the compacting device and the operating cycle of the unloader.

It is a further object of the invention to provide an effective and efficient means for controllig the operation of a compacting device.

Other objects and advantages will be apparent from or pointed out in the following description and accompanying drawings.

SUMMARY OF THE INVENTION The present invention relates to a mobile compacting device capable of compressing a variety of different materials into dense blocks or bales. This is accomplished by providing means for selecting different cycles of operation in a multi-stage compactor and a means to readily shift into the most efficient and effective mode of operation for each type of material to be compacted.

More particularly, the invention provides a single compacting apparatus which may be used for both refuse and snow and having different modes of operation for each type of material. The present invention also provides for a separate mode of operation to handle ice.

The mobile unit of the present invention includes a feeding conveyor at the forwardmost part thereof. When the unit is to be used for compacting refuse, a hopper is detachably secured to the forward end to partially enclose feeding conveyor. Since the feeding conveyor is located immediately adjacent to the roadway, the conveyor and hopper are easily accessible for the deposit of refuse therein.

The operators station from which all functions of the mobile unit may be controlled, is located at the forward end of the vehicle directly above the elevating conveyor and laterally centered with respect to the vehicle chassis. This arrangement maximizes visibility and provides a clear view of the area immediately in front of the feeding conveyor. Such a view is very important in municipal snow removal operations where obstructions such as curbs and sidewalks must be avoided.

An unloader conveyor is attached near the rear of the unit and is adapted to transport blocks of compressed material from the mobile unit to a waiting truck which follows behind the unit. The conveyor includes an upright lift section having a bucket guidably moveable along the length thereof. In its lowermost position the bucket will receive a block of material as it is discharged from the final compression chamber of the compacting device. After the block has entered the bucket, motor means associated with the unloader are energized to move the bucket upwardly along the lift section. When the bucket reaches the uppermost end of the lift section, it is automatically tilted, discharging the block onto a transport conveyor extending generally horizontally to the rear. The arrangement is such that the transport section of the unloader will extendover the cab of a conventional truck following behind the mobile unit. The free end of the transport section will be disposed over the body of the truck to discharge compressed blocks of material thereinto.

Control means are provided for achieving a coordination between the cycling of the compacting device and the operation of the unloader. This control means will prevent a block from being discharged from the compacting device if the unloader bucket is not in position to receive the same. Also, the control means prevents upward movement of a loaded bucket if there is insufficient space for the block on the upper transport section. In such event, the control means will also prevent the compacting apparatus from discharging another block toward the already'loaded bucket.

The lift section of the unloader is pivotally attached to the vehicle chassis and the transport section is pivotally attached to the lift section. This permits a folding retraction of the unloader toward the vehicle chassis when not in use. Y

The compacting device itself includes a plurality of compression chambers, the first of which is a charging chamber having an upper, open side. The charging chamber receives loose material from the elevating conveyor whereupon the material is moved toward a confined space by a pusher plate. Associated with the pusher plate is a moveable closure plate which closes the open side of the charging chamber as a pusher plate moves therethrough. The closure plate prevents mate rial from entering the area behind the pusher plate as the pusher moves through its stroke. The curved configuration of the closure plate causes snow entering the compacting device to be directed into the charging chamber. The arrangement is such, that even with a constant supply of loose material impinging upon the surface of the closure, there is very little resistance to movement of the closure in a direction either to cover the open side of the charging chamber or to uncover the same.

The electrical and hydraulic systems for controlling the operation of the compacting device include numerous important features including a means for returning all the hydraulic fluid in the various systems directly to the reservoir so as to reduce the loads on the various pumps during start-up, a means to ensure that the block of compressed material exiting from the compacting device is cut off squarely and a means to prevent any possible dead heading of the moveable compacting members.

BRIEF DESCRIPTION OF THE DRAWING FIG. 1 is a general side elevational view of a mobile compacting apparatus embodying a preferred form of the present invention;

FIG. 2 is a front elevational view of the mobile compac'ting apparatus shown in FIG. 1;

FIG. 3 is a fragmentary side elevational view of the mobile compacting apparatus of FIG. 1 showing the mounting of a detachable hopper on the apparatus;

FIG. 3a is a fragmentary perspective view of the forward end of the mobile compacting apparatus of FIG. 1 showing a modification thereto;

FIG. 4 is a fragmentary front elevational view of the apparatus shown in FIG. 3;

FIG. 5 is a fragmentary front elevational view including a cut-away section of. the compacting device of the mobile vunit of FIG. 1

FIG. 5a is a perspective detail view of the curved closure plate of the compacting device of FIG. 5;

FIG. 6 is a schematic diagram of the hydraulic control circuit and associated elements for the compacting device of the mobile unit of FIG. 1;

FIG. 7 is a schematic wiring diagram of the electrical control means for automatic cycling of the compacting device of the mobile unit of FIG. 1;

FIG. 7a is an elevational view of a selector switch for shifting the mode of operation of the compacting device;

FIG. 8 is a schematic wiring diagram of a system dump control used during start-up of the hydraulic system of the mobile compacting apparatus shown in FIG.

FIG. 9 is a fragmentary side elevational view of the unloader conveyor of the mobile compacting apparatus of FIG. 1 with solid lines showing the retracted position of the unloader and phantom lines showing the extended position thereof;

FIG. 10 is a fragmentary vertical sectional view taken on the line 10-10 of FIG. 9;

FIG. 11 is a fragmentary horizontal sectional view taken on the line l11ll of FIG. 9;

FIG. 11 is a fragmentary vertical elevational view of one cam for tilting the bucket, taken on the line 12-12 of FIG. 10-,

FIG. 13 is a schematic wiring diagram of the electrical control means provided for automatic cycling of the unloader shown in FIGS. 9 through 12 and for coordinating therewith the operation of the compacting device of the mobile unit of FIG. 1.

CROSS REFERENCE TO RELATED APPLICATIONS This is an improvement of the device disclosed in copending US, patent application Ser, No. 204,533, filed Dec. 3, l97l,now US. Pat. No. 3,765,321, issued Oct. 16, 1973 which is a continuation of application Ser. No. 829,229, filed June 2, I969 and now abandoned. The instant application and aforementioned two applications all have a common assignee.

DETAILED DESCRIPTION OF THE DRAWING Overall Mobile Unit Like numerals among the various figures of the drawing and the following description thereof refer to like elements and/or structure.

Referring to FIG. I, there is illustrated a vehicle chassis designated generally as having frame members 21 which are also illustrated in FIG. 11. The chassis includes a pair of steerable wheels 22 disposed adjacent to the forward end thereof. These steerable wheels 22 are forwardmost ground engaging means facilitating forward movement of the device. Adjacent to the rearward end of the chassis 20 are disposed a plurality of driving and support wheels 24. Preferably, three axels are used in conjunction with the wheels 24.

A compacting device 26 similar to that disclosed in the aboveddentified abandoned and co-pending applications for patent, is mounted adjacent to the rearward end of the chassis 20 directly above the wheels 24. At the extreme rearward end of the chassis 20 is mounted a foldable unloader conveyor referred to generally by reference numeral 28. The construction and operation of both the compacting device 26 and the unloader 28 will be described in greater detail hereinafter.

An engine driven pump assembly is designated by reference numeral 30. The assembly is centrally located on the chassis 20 and includes a plurality of individual pumps. Located on the chassis forwardly of the pump assembly 30 is a vehicle drive engine 32 which serves as a propulsion means for the mobile unit.

At the forwardmost end of the vehicle chassis there is mounted a feeding conveyor 34, the details of which are best seen in FIG. 2. This conveyor has a plurality of paddle blades 36 carried by a pair of endless chains 38. The chains 38 are carried by a set of front sprockets 40 which are drivingiy secured to a cross shaft 42 journalled at the front-end of the apparatus. An additional set of sprockets (not shown), disposed rearwardly of the sprockets 40, also carry chains 38, to permit endless movement thereof.

The feeding conveyor 34 includes auger-type conveyors 44 at opposite sides of the paddle blades 36 and secured to the cross shaft 42 for rotary movement therewith, The outer diameter of each auger corresponds to that of the arc defined by the outer edges of the paddle blades 36 as they pass over the peripheries of the sprockets 40. The feeding conveyor is power driven to effect rotation of the sprockets 40 and cross shaft 42 which, in turn, effect rotary drive of the auger conveyors 44 to move material inwardly toward the paddle blades 36. During operation, the blades 36 move rearwardly on the lower sides of the sprockets to feed material to an elevating conveyor 46. The feeding conveyor 34 is so disposed with respect to the vehicle chassis as to constitute the forwardmost portion of the mobile unit. Also, the feeding conveyor is located closely adjacent to the ground or roadway upon which the mobile unit travels. The location is such that the cross shaft 42 may be adjusted to a position entirely below the vehicle frame 21.

Side arms 50 are pivotally connected to a supporting structure 52 which, in turn, is connected to the vehicle chassis 20. The feeding conveyor 34 is partially supported by the arms 50 so that vertical swinging movement of the arms, which is effected by hydraulic cylinder 54 operating through linkage system 55, results in vertical movement of the feeding conveyor 34 for height adjustment thereof. Springs 56, in the linkage system 55 provide a free floating arrangement for the feeding conveyor to permit vertical deflection thereof when an obstruction is encountered.

The elevating conveyor 46 extends rearwardly from the feeding conveyor at an upward incline so that the discharge end 57 thereof is disposed directly over the entry opening 58 of the compacting device 26. The elevating conveyor 46 is of the endless belt type having a longitudinally extending conveyor belt 59 carried be tween opposed side panels 60.

Certain general aspects and structural details of the feeding conveyor 34 and the elevating conveyor 46 are similar to those shown and described in US. Pat. NOS. 2,776,036 and 2,669,338 to R. W. Kling and US. Pat. No. 2,639,022 to R. D. MacDonald.

The vehicle prime mover includes a power takeoff shaft (not shown) coupled to a double pump 6] disposed under the elevating conveyor 46. The conveyor pump is of the single inlet, double outlet type, with each outlet thereof supplying pressure to separate hydraulic branches-The pressurized hydraulic fluid in a first conveyor branch line 62, drives a hydraulic motor 63 and associated transmission 64 to supply power to the feeding conveyor 34. The pump 61 supplies pressure to a second conveyor branch line 66 through the other pump outlet. This second conveyor branch line 66 supplies pressurized fluid to a hydraulic motor 68 near the end 57 of the elevating conveyor 46, motor 68 driving transmission 70 which in turn drives the conveyor belt 59 of the elevating conveyor.

In order to facilitate the gathering of material into the feeding conveyor and to prevent material from being spilled around the edges thereof, or from flowing rearwardly thereof, a scoop assembly 72 is provided. The scoop assembly 72 includes a bulldozer-type moldboard 74 disposed transversely to the vehicle chassis and immediately rearwardly of the forward augers 44 and sprockets 40 of the feeding conveyor 34. Also included as part of the scoop assembly 72 are detachable sideboards 76, disposed adjacent to the outside ends of each auger 44. The moldboard 74 has a curved incline with respect to the vertical and is adapted to gather material into the feeding conveyor 34 during forward travel of the mobile unit. The Sideboards 76 also direct material toward the feeding conveyor and prevent material from flowing around the lateral ends of the moldboard 74. The moldboard 74, of course, prevents material which has entered into the feeding conveyor 34 from escaping by flowing rearwardly toward the front wheels 22 of the vehicle chassis.

FIG. 3a illustrates an alternate structure 72a to the scoop assembly 72. Here, the augers 44 have been removed and the scoop assembly has been replaced by a pair of gatherer blades 79. The gatherers 79 are disposed at a rearwardly converging incline with respect to each other, so that during forward travel of the mobile unit, material in the path of the gatherers will be directed inwardly toward the paddle blades 36.

The choice implements to be used with the feeding conveyor 34 for gathering material thereinto, depends on the nature and condition of the material to be gathered. For example, in snow removal operations, it has been found that the scoop assembly 72 is the most efficient implement for gathering snow which has been plowed into piles or windows. However, for gathering unplowed snow from a street or roadway, the gatherer blades, as illustrated in FIG. 3a, have been found to be the most efficient.

The above described arrangement of hydraulic cylinders 54 and associated linkage 55 for raising and lowering the feeding conveyor, will also raise and lower the scoop assembly 72 on gatherers 79 along therewith. However, additional means are provided for indepen dently raising or lowering the scoop assembly 72 or gathers 79. The scoop adjustment means includes a hydraulic cylinder 80 disposed laterally opposite the above-mentioned hydraulic cylinder 54. Hydraulic cylinder 80 operates linkage means 82 which is connected to the scoop 72 or gatherers 79. The scoop or gatherer implement is pivotally connected to the vehicle chassis so that movement of the linkage means effects vertical adjustment of the implement.

In operation, the height of the scoop, or gatherer implement, and the height of the overall feeding conveyor assembly may be adjusted such that the latter is disposed adjacent a roadway and such that the implement will contact or nearly contact the roadway. With the feeding conveyor and scoop, or gatherer implement, so positioned, the mobile apparatus is ideally suited for snow removal. The scoop, or gatherer implement,

broadens the path from which snow is fed into the feeding conveyor as the mobile unit moves forwardly, and also serves to scrape up the lower layers of snow adjacent to the ground or roadway, and directs-this snow into the feeding conveyor. The feeding conveyor 34 will move the snow to the lower end of the elevating conveyor 46 which then transports the snow to the upper end of the conveyor and discharges it into the top entry opening 58 of the compacting device. The snow is compressed into dense blocks in the compacting device which discharges the same to the unloader 28. The unloader conveys the blocks to the body of a truck following behind the mobile unit.

As seen in FIGS. 3 and 4, a hopper 84 may be detachably mounted on and secured to the scoop 72. The hopper 84 includes an end panel 86 which acts as an upward extension of the moldboard 74 of the scoop 72. Side panels 88 of the hopper act as. upper extensions of the sideboards 76 of the scoop. The hopper includes a bottom panel 90 extending forwardly from the moldboard 74 at a curved, upward incline. The curved configuration of panel 90 provides the hopper with a contour which correspondns to the abovementioned are described by the outer edges of paddle blades 36. It is to be understood, however, that some clearance exists between the paddle blades and the hopper. The contour of hopper panel 90 prevents material from being trapped at the bottom of the hopper and assures that all material entering the hopper will pass into the feeding conveyor. I

The hopper also includes a set of outwardly inclined panels 93, 94, forming a flared opening 96 into the hopper 84. Panel 93 which is joined at the uppermost edge of front panel 90, extends forwardly at upward slope which is more gentle, with respect to the horizontal than the slope of panel 90. Each of the panels 94,95 are joined to the forwardmost edge of one of the side panels 88 and diverge outwardly in a forward direction.

The hopper is secured in position by several bolts 98, and is readily detachable upon removal of the bolts. In position, the hopper forms a complete enclosure for the feeding conveyor except for its top opening 100 defined by the free edges of panels 86, 88, 93, 94, and 95. This top opening 100 includes the aforementioned flared opening 96.

When the mobile unit travels between work areas, the feeding conveyor 34, scoop 72, and hopper 84 (if attached) are raised to an upper vertical position as shown in FIG. 3 to provide a clearance with respect to the ground or roadway. As mentioned above, this raising and lowering is accomplished by a hydraulic cylinder 54 acting through linkage 55. The cylinder 54 is controlled through a power unit 103, to be described hereinafter.

Attachment of the hopper 84 to the scoop 72 (along with a shifting of the cycle of the compacting device as will be described later herein) adapts the mobile unit to render it ideally suitable for the collection and compaction of solid waste or refuse. For this reason, the combined hopper, scoop and feeding conveyor will be referred to as the refuse intake means. As just mentioned, this entire intake means may be vertically adjusted by actuation of hydraulic cylinder 54. However, in the alternative, the scoop 72 and attached hopper, may be vertically adjusted independently of the feeding conveyor by actuation of hydraulic cylinder 80. Using either means of adjustment, the refuse intake means may be vertically positioned so that the scoop and attached hopper contact the ground to rest thereon. In this ground engaging position the top opening 100 and flared opening 96 of the hopper are close enough to the ground that the contents of any conventional truck can be dumped or otherwise moved directly into the hopper without the need for elevating any of the material above the level of the truck body. The rearward edge of a conventional dump body actually lowers as the forward part of the body swings upwardly. In the apparatus of the present invention, the height of the lower edge of the flared opening 96 of the hopper 84 is positionable at a level below the rearward edge of a conventional dump truck body when the truck body is in the raised position. This relationship also holds true when the entire refuse intake means is raised slightly from the ground. Also, in either the ground-engaging position or the slightly raised position of the intake means, the lower edge of the flared opening 96 (i.e., the upper edge of panel 93) will be disposed below the vehicle frame members 21.

This low positioningof the intake means also greatly facilitates the use of the mobile unit in conjunction with human workers, since the intake means is within easy reach of the average human. With the intake means in the ground engaging position, or slightly raised therefrom, the lower edge of the flared opening 96 will be at knee-level of an average human. Even with the intake means fully raised for travel, this lower edge will not move above waist level of an average human. In no position of the intakemeans will any part thereof reach the level of the cab or operators station 105 or the level of the entry opening 58 of the compacting device 26.

Pressurized fluid for both hydraulic cylinders 54 and 80, used in adjusting the various front-end components, is supplied by the above-mentioned double pump 61 driven by a power take-off shaft (not shown) from the vehicle engine 32. The various systems driven by this pump, namely, the first conveyor branch line 62, the second conveyor branch line 66, and the lines to cylinders 54 and 80 are all connected with a modular power unit 103 disposed at the side of the mobile unit adjacent the vehicle engine 32. The power unit 103 includes a reservoir for the various lines connected therewith and serves as a situs for installation of the major valves and associated plumbing to control the operation of the systems receiving hydraulic pressure from pump 61.

An operators station, referred to generally by reference numeral 105, is mounted adjacent the forward end of the vehicle and directly above the elevating conveyor 46 by means of support structure 52. The entire operators station 105 is disposed forwardly of the front, steerable wheels 22, and entirely above the level of the feeding conveyor 34 at all vertical positions thereof. The operators station includes a main enclosure portion 107 and extension enclosure portion 109. The positioning of the operator's station above the con: veyors is such that avertical plane bisecting the main enclosure portion 107 coincides with a vertical plane bisecting the feeding conveyor 34 and the elevating conveyor 46. Since the drivers controls for operating the mobile unit in its vehicular aspects (such'a's the steering wheel, throttle, brake, etc.) are disposed main enclosure portion with respect to the feeding and elevating conveyors, affords the operator a clear view of the roadway or ground both ahead of and also immediately to both sides of the feeding conveyor. This is particularly important where material, particularly snow, is being removed from city streets having obstructions, such as curbs, which are difficult to see from pacting device 26. Station also includes operators I controls for controlling the unloader 28 in its conveyor functions and extension and retraction functions.

A television camera having an automatic pan and tilt control may be positioned on the mobileunit so as to provide, on a viewing screen at the operators station,

a commanding rear view.

The mobile compacting apparatus may be adapted for gathering and compacting leaves by replacing the paddle blades 36 of the feeding conveyor with rotary brushes. In this case, the cycle of operation of the compacting device is the same as the solid waste cycle which will be described hereinafter.

When the mobile compacting apparatus of the invention is to handle solid waste, leaves or similar loose ma-- terials, a canopy-type cover is provided over the elevating conveyor 46 to retain the material within the conveyor.

CONSTRUCTION OF THE COMPACTING DEVICE AND ONE OPERATING MODE THEREOF The operation and construction of the compacting device 26 mounted on the chassis 20 of the mobile unit will now be described. In describing the operation of the compacting device in conjunction with the construction thereof, reference will be made to an operating cycle primarily intended for compacting snow. It will be understood, however, that the present invention provides for operating cycles other than the snow compacting cycle, which cycles will be further described hereinafter.

As described above, loose material to be compacted first passes through a feeding conveyor 34 which transports the material to the elevating conveyor 46, the latter discharging the material into the entry opening 58 at the top of the compacting device 26. This discharged material falls into receiving chamber 112 (FIG. 5).

Referring to FIG. 5 for the details on construction of the compacting device 26, a pusher plate 114 is actuated'by a pair of cylinders 115, 116 which are oppositelydisposed on either side of the devices to move material to the right and simultaneously compact it. It

is to be noted that FIG. 5 shows only one pusher cylinder l16,'the pair being shown schematically in'F IG. 6.

At the right-hand end of the machine, as seen in FIG. 5, cylinders 117, 118 actuate a pair of tampers 119, 120 to compress the material further and press it down in front of ram 121, the head of which is seen in phantom lines in FIG. 5. Again, FIG. 5 shows only one of the tampers 120 and its associated cylinder 118, the pairs being'shown schematically in FIG. 6.

Ram 121, as it further compresses the material which has now entered ram chamber 122, also moves the material beyond the area of tamping and against the gate 124. When the material has been sufficiently compacted, gate 124 is opened by hydraulic cylinder 126. Upon further cycling of the ram the firmly compacted block of material will be ejected through the open gate. Ejection is accomplished by adding less compacted snow behind the firmly compacted block. When the desired length of compacted block clears the path of movement of the gate 124, cylinder 126 drives the open gate 124 toward its closed position shearing off the projected portion of the block. This sheared-off block is then received in the unloader conveyor 28 (FIG. 1) which transports the same into a waiting vehicle. The pusher plate 114, tampers 119, 120 and ram 121 are referred to collectively as the moveable compacting members.

For purposes of illustration, gate 124 and its associated elements have been shown in FIG. 5 to be located on the side of the compacting device facing the viewer. However, the gate 124 of the compacting device 26 shown on the mobile apparatus of FIG. 1 is located on the side of the compacting apparatus which would face away from the viewer in FIG. 5. In either case it is to be understood that forward movement of the ram for compressing material in the ram chamber will always be toward the gate 124.

The pusher plate 114 includes a closure plate 129 of curvilinear configuration. The shape of the plate is best seen by reference to FIG. 5a illustrating a perpsective view thereof. Closure plate 129 includes a mounting bracket 131 by which it is pivotally attached to a cooperating bracket 133 at the upper edge of the pusher plate 114. Both the pusher plate 114 and closure plate 129 extend transversely across substantially the entire width of the receiving chamber 112.

A roller 135 extends transversely across the receiving chamber 1 12 at the upper left-hand corner thereof (referring to FIG. 5).

A pivotably mounted cleaning blade 136 also extends across the receiving chamber 112 in closely spaced relationship with the roller 135. Cleaning blade 136 will serve to remove from the closure plate 129 any material which has the tendency to adhere thereto. This prevents the jamming of material between the plate 129 and the blade 136, as the plate moves in the space between the blade 136 and the roller 135. Motion is imp'arted to the closure plate by movement of the pusher plate through its stroke. The roller 135 guides the movement of the closure plate 129 through an arcuate path as the pusher plate moves between its extreme positions. FIG. 5 illustrates the relative positions of the pusher plate 114 and closure plate 129 at these extreme positions.

The area wherein snow is initially compressed by the pusher plate 114 will be referred to as the charging chamber 139. Charging chamber 139 includes first chamber portion 140 defined by the path of movement of the pusher plate 114 between its extreme positions and a second chamber portion 14] extending from the extreme right-hand end position of the pusher gate (referring to FIG. 5) to the edge of chamber 144, the latter being defined by the path of movement of the tampers 119,120. The uppermost side of chamber portion 141 is permanently closed by wall 143. In contrast, the uppermost side of chamber portion 140 is progressively opened and closed as the pusher plate 1 14 moves back and forth in this chamber portion. The purpose of the closure plate 129 is to permit a continuous reception of material into the chamber 112 by preventing material from falling behind the pusher plate 114 as the pusher plate advances toward the right-hand, extended position shows in phantom lines in FIG. 5. The particular configuration and arrangement of the closure plate is such as to minimize resistance to the movement of the pusher plate and the closure plate itself, and to aid in directing loose material into the charging chamber.

In FIG. 5, solid lines indicate the position of both the closure plate 129 and pusher plate 114 in their retracted, or extreme left-hand end positions. With the pusher plate retracted, the upper side of chamber portion 140 is completely open for the reception of snow. When the pusher plate advances, the closure plate is pulled thereby through the clearance 137 between roller and blade 136 to close off the area through which the plate 114 has moved. In no position of the pusher plate during its advancing movement is there a need for the closure plate to displace any material which has been received in the chambers 112 or 139. Instead, the curvature of the closure plate directs any material impinging thereon into the chamber 139 to be compressed and moved by the pusher plate.

When the pusher plate 114 reaches the fully extended, or extreme right-hand position, the closure plate 129 has now closed off the entire upper side of chamber portion 140. This progressive closing prevents any snow from falling behind the pusher plate. With the pusher plate now in its fully extended or nearly extended position, some of the material which is being continuously fed into chamber 112 will collect above the closure plate 129. As the pusher plate is retracted and the closure plate moves back through the roller 135 and blade 136 to progressively open the chamber portion 140, the slope of the closure plate will increase and the curvature thereof will cause the collected material to be directed through the expanding opening into the chamber 139. This material, of course, will then be compressed by the next stroke of the pusher plate.

As mentioned above, hydraulic cylinders 115, 116, disposed opposite to each other on either side of the compacting device drive the pusher plate 114. The pusher plate is provided with extensions 147 passing through slots 149 at opposite sides of the end walls 151 of the compacting device 26. Piston rods 153, 154 of cylinders 115,116 are pivoted to the extensions 147. Phenolic ways are disposed about the slots 149 to minimize friction and provide a smooth operation as the extensions 147 move along the length of the slots.

HYDRAULIC CIRCUITRY The hydraulic circuitry for operating the compacting device 26 and unloader conveyor 28 is schematically illustrated in FIG. 6. Pressurized fluid is supplied to the system by four separate pumps, namely, double pumps 157, 159 and 161, and single pump 163. Each of the double pumps have a single inlet and two outlets which are joined together in parallel, while the single pump has a single inlet and single outlet. All of the pumps, 157,159,161 and 163 are part of the pump assembly 30 and are driven by an engine, referred to as the compressor engine, which is separate from the vehicle engine and which is also part of the pump assembly housing.

The overall hydraulic circuit actually comprises four separate hydraulic systems connected to a common reservoir, each system having its own pump, filter and valves. The system for driving the ram 121 is illustrated schematically at the left hand portion of FIG. 6. In this system, hydraulic fluid from the reservoir passes through filter 165 into the inlet side of double pump 157. The two outlets from pump 157 are joined in parallel so that all the output therefrom flows through pressure line 167 into directional control valve 169. This valve is actuated by two solenoids 170, 171 and includes an open or tandem center spool as do the other control valves. When neither solenoid is energized, the valve will be in the center condition wherein pressurized fluid from pump 157 is directed back to the reservoir via exhaust line 173 and wherein hydraulic fluid is trapped in both chambers of the double acting ram actuating cylinder 175. When solenoid 170 is actuated, pressurized fluid from the pump 157 will be directed through conduit 177 into chamber 179 causing the piston rod 181 to extend from the cylinder, in turn, causing the ram 121 to move in the direction of compact material against the closed gate 124. Decnergizing solenoid 170 and energizing solenoid 171 then causes pressurized fluid to be directed through the valve and into cylinder chamber 183 via conduit 185. Pressurized fluid in chamber 183 causes the piston rod 181 to retract which in turn effects movement of the ram 121 through its return stroke. The valve 169 in this condition effects communication between conduit 177 and pressure line 173 so that, as the ram is returning, fluid in chamber 179 will flow back to the reservoir. Likewise, when the ram is advancing, the valve 169 will cause fluid in chamber 183 to be diverted back to the reservoir.

The hydraulic system for the ram includes electrically controlled relief valve 187 which is connected to the pressure line 167 to open the pressure line to communication with the reservoir upon actuation thereof. Valve 187 includes a solenoid actuation means and may be utilized during the start up operation as will be described later.

Because of the large volume of fluid flowing out of chamber 179 of the ram actuating cylinder 175 as the piston rod 181 is being retracted, a bypass line 189 is provided around the valve 169 to prevent a possible internal shock to the valve. Line 189 includes a flow restriction device 190 such as a needle valve to meter the return flow. The line also includes a one way check valve 191 to prevent pressurized fluid in line 167 from flowing through the bypass line 189.

The hydraulic system for the tampers is basically the same as that for the ram except for the provision of a separate hydraulic branch including a separate directional control valve for each of the two tamper actuating cylinders 117, 118. In the tamper system, fluid flows from the reservoir across filter 192 and into the single inlet of double pump 159. Each of the two outlets from pump 159 has a separate pressure line 193, 194 connected therewith. Each pressure line 193, 194 is connected with a directional control valve of the type described in the foregoing discussion of the ram system. Valve 195 is actuated by solenoids 197 and 198 and valve 196 is actuated by solenoids 199 and 200. When the solenoids of each valve are de-energized so that each valve assumes its center condition, pressurized fluid in line 193 will be directed by valve 195 into exhaust line 201 for return to the reservoir. At the same time, valve 196, in its central condition, causes pressurized fluid in line 194 to be directed into exhaust line 202 back to the reservoir. Also, with both valves in their de-energized, or central conditions any fluid in chambers 203 and 205 of double acting cylinder 117 of tamper 119, any fluid in chambers 207 and 209 of double acting cylinder 118 of tamper will be blocked from flowing out of these chambers by each of the valves 195 and 196. When solenoid 197 of valve 195 is actuated, pressurized fluid from line 193 will flow through the valve into conduit 211 and from there into chamber 203 to extend piston rod 213 and move tamper 119 downwardly through its advancing stroke.

At the same time, energization of solenoid 199 of valve 196 effects communication between pressure line 194 and conduit 215 thereby causing fluid to enter the chamber 207. Pressurized fluid in chamber 207 will effect extension of piston rod 217 to drive the tamper 120 through its downwardly advancing stroke. Deenergization of solenoids 197 and 199 together with energization of solenoids 198 and 200 effects reversal of both tampers. In this condition, valve 195 will direct pressurized fluid from line 193 into conduit 219 and thence into chamber 205 communication therewith. At the same time, valve 195 opens communication between line 211 and exhaust line 201 so that as the tamper is passing through its return stroke and the piston rod 213 is retracting, fluid in chamber 203 may flow back to the reservoir. Fluid is exhausted from chamber 205, of course, during the advance stroke of tamper 119. This fluid is directed from conduit 219 by valve 195 into exhaust line 201.

Energization of solenoid 200 of valve 196 causes fluid from pressure line 194 to flow through the valve into conduit 221 and thence into chamber 209. Pressurized fluid in chamber 209 causes the piston rod 217 to retract, moving tamper 120 through its return stroke. At the same time, valve 196 has opened communication between conduit 215 and exhaust line 202 so that spent fluid from chamber 207 will be driven out into conduit 215, through valve 196 into exhaust line 202 and thence into the reservoir. Fluid is exhausted from chamber 209, of course during the advance stroke of tamper 120. This fluid is directed from conduit 221 by valve 196 into exhaust line 202.

As in the case of the ram system, each of the branch lines for driving the tampers includes a relief valve which is electrically controlled. Thus, pressure line 193 has connected thereto, relief valve 222 which communicates with the reservoir. In like fashion, relief valve 223 is connected to line 194 and also communicates with the reservoir.

In the hydraulic system for driving the pusher plate 114, hydraulic fluid passes from the reservoir through filter 225 into the single inlet of double pump 161. The flows of pressurized fluid from the two outlets of pump 161 are combined in line 227 which is connected with the pump outlets. Line 227 communicates with directional flow control valve 229, a four-way valve, similar to the others, and having actuating solenoids 230 and 231. As in the case of the other control valves, deenergization of both solenoids effects communication between the pressure line 227 and the exhaust line 233 between the valve and the reservoir. As is also the case with the other valves, de-energization of the solenoid blocks the lines leading to and from hydraulic cylinders 115,- l to which drive the pusher plate 11 2.

When the solenoid 23%- is energized the valve 229 will effect communication between pressure line 227 and conduit 238. The flow in conduit 238 is divided into two branches 239 and 24 t), brunch 239 feeding pressurized fluid to chamber 241 of cylinder H5 and branch Z-lrOfeeding pressurized fluid to chamber 242 of cylin der 116. The pressure in chamber 24.; will effect extension of the piston rod 253 outwardly from the cylinder 115 while the pressure in chamber 2- .2 simultaneously effects extension of the piston rod l54 outwardly from cylinder llo. This extending motion of the piston rods 153, 154, effects retraction of the pusher plate, i.e. movement of the pusher plate through the return portion ofits stroke from the phantom line position in H6. 5 to the solid line position therein. De-energization of solenoid 230 and energization of solenoid 23?. the valve 229 will effect movement of the pusher plate in the opposite direction. in this condition, the valve 229 will effect communication between pressure line 227 and conduit 246. in conduit 2 .6, the flow of pressurized fluid is divided into branches 247 and 248 each branch having a pressurecompensated flow control 249, 250 respectively, which will tend to keep the movement of the piston rods E53, 54 in cylinders HS and lid in sequence with each other during extension and retrac tion. Branch 248 feeds chamber 25% and branch 24.7 feeds chamber 252 to effect retraction of piston rods 153, 154 and movement of the pusher plate through the advancing portion of its stroke, i.e., from the left to the right of FIG. 5.

At the same time, fluid is being forced out of chambers 24!. and 232 into branches 2.39 and 24,6 respectively and then from there, the respective flows join together in conduit 238 wherein the fluid flows back to valve 229. Valve 229 effects communication between conduit 233 and exhaust line 233 for return of the spent fluid to the reservoir. ln like fashion, when the pusher plate is mo ing in the opposite direction, i.e. in the retracting through branches 247, 248 respectively, the flows of which join in conduit 2%. Valve 229 will direct the return flow in conduit 2% to exhaust line 233 which returns the spend fluid to the reservoir.

Electrically energized relief valve 254 will serve to vent hydraulic fluid in pressure line 227 to the reservoir when an electrical signal is received.

The last system within the hydraulic circuitry of Fit]. 6 includes a singie pump E63 receiving fluid which has passed from the reservoir through filter 2% and into the pump inlet. Pressurized fluid passes from the single outlet of pump 163 flows into pressure line 25%; which is connected with control valve 2ft). When the sole noids 261., 262 of the valve 26%) are tie-energized to place the valve in the center condition, fluid from line 25f, will be directed by valve 260 into feed line 26 -3 which connects with an additional control valve 266.. In like fashion, when solenoids 2 87., 268 of valve 266 are both de-energized valve 266 will also assume the center condition wherein the valve directs pressurized fluid from feed line 264 into feed line 27% which is con nected with an additional directional control valve 272.. With solenoids 273, 274 of valve 272 in the deenergized condition, and thus, with valve 272 in the center condition, pressurized fluid from line 2741 will be directed by valve 272 into exhaust line 27s which returns the fluid to the reservoir. As in the case of the other directional control valves, fluid in the chambers of the hydraulic cylinders controlled by valves 260, 266 and 272 will be trapped therein due to the blockage by each valve of the conduits leading to each chamber of the respective cylinders. This will lock the piston rod of each cylinder in position.

Valve 272 controls the operation of cylinders 278, 279 which operate the folding extension and retraction of the unloader conveyor 28.. Valve 266 controls cylinder 280 which powers the actual bucket movement of the unloader assembly. The structure and operation of the unloader conveyor 28 will be described in detail hereinafter.

Valve 266 controls the forementioned cylinder l26 which operates gate 124 in the manner described earlier.

Control valve 272 is normally in the de-energized, center position so that under most conditions the valve serves to direct spent hydraulic fluid from cylinders 126 and 288 into exhaust line 276 to return the fluid to the reservoir. in this normal condition, piston rods 282, 283 of cylinders 278, 279 will be locked in position.

However, when it is desired to extend the unloader for use, solenoid 273 will be energized causing pressurized fluid to enter chambers 284, 285 via conduits 286 effecting extension of the piston rods 282, 233. This, in turn, effects a retraction or foldingin of the unloader toward the mobile unit. Actuation of solenoid 274 shifts the valve so that pressure is now fed into chamoers 238, 289 via conduits 290 causing piston rods 282, 283 to retract which, in turn, causes the unloader to extend outwardly from the mobile unit for use. During this last mentioned movement, fluid from chambers 284, 285 is being exhausted through conduits 286 and directed by valve 272 into exhaust line 276 for return to the reservoir. During movement in the opposite direction, for retracting the conveyor, fluid from chambers 288, 289 is being exhausted through conduits 290 and directed by valve 272 into the exhaust line 276 for return to the reservoir. When the piston rod 282 of cylinder 278 has reached the desired position wherein the unloader is either fully extended or fully retracted, the appropriate solenoid 273 or 274 will be deenergized locking fluid into both sides of the cylinder thereby locking the unloader in position.

To move the bucket of the unloader, solenoid 268 of valve 26 6 is energized causing the valve to direct fluid into conduit 292 which, in turn, sends the fluid into chamber 294 of the cylinder 28%). This effects an upward movement of piston 4741 to move mechanical means (to be described hereinafter) for raising the bucket. D e-energizing solenoid 263 while energizing solenoid 267 admits fluid under pressure into chamber 25 E via conduit 3M? reversing the movement of piston 4 78 to in turn reverse the movement of bucket 298. During this reverse movement, fluid from chamber 294 will be exhausted through conduit 292 and directed by valve 266 into line 27) for ultimate return to the reservoir. During the upward movement of piston 47:), chamber 299 will be exhausted through conduit 300 and directed by valve 25:6 into line 270 for eventual return to the reservoir. The disposition of the cylinder in the schematic arrangement of PEG. 6 is not intended to depict actual disposition of the cylinder with respect to use of the terms upward and downward".

Energization of solenoid 261 of valve 260 feeds fluid into chamber 302 of cylinder 126 via conduit 304 to extend piston rod 306 moving the gate 124 to a closed position. Energization of solenoid 262 shifts valve 260 to direct pressurized fluid from line 258 into conduit 308 and then into chamber 304. This causes retraction of the piston rod 306 moving gate 124 to the open position while fluid is exhausted from chamber 302 into line 304 and directed by valve 260 into line 264 for eventual return to the reservoir. When the piston rod 306 is moving in the gate closing direction, fluid is exhausted from chamber 309 through line 308 and directed by valve 260 into line 264 for return to the reservoir.

Relief valve 310 is of the same type as relief valves 187, 222, 223 and 254. This valve will open communication between pressure line 258 and the reservoir when electrically actuated.

It will be understood that when either of the solenoids of any one of the three valves 260, 266 and 272 are actuated to operate the cylinder associated with that one valve, the other two valves will be in the deenergized central condition to permit the flow of hydraulic fluid to and from the one actuated valve. it will also be understood that all of the above mentioned control valves, namely valves 169, 195, 196, 229, 260, 266 and 272 are four-way solenoid actuated valves, each having an open or tandem center spool.

ELECTRICAL CONTROL CIRCUITRY Reference is now made to FIG. 7 which shows a schematic wiring diagram of the control circuitry for the compacting device 26 and unloader 28 of the present invention. As depicted therein, a generator or alternator from the compressor engine supplies 120 volts AC through a magnetic-type breaker 312 to furnish power to electrical supply lines 314 and 315. Prior to closing the breaker 312 tov energize the electrical system, switch 318, which is moveable between start" and run positions is placed in the start position to open this switch. Thus, when the breaker 312 is closed to supply power to lines 314, 315, the system dump relay 320 will remain tie-energized and its closed contacts 321-325 (see FIG. 8) will remain closed.

Closing of the breaker 312 also supplies electrical power to the circuitry of FIG. 8 so that, with switch 318 in the start position, solenoids 326-330 will receive power across closed contacts 321-325 respectively, thereby energizing each solenoid.

Energized solenoids 326-330 actuate aforementioned valves 187, 222, 223, 254, and 310 respectively (see FIG. 6) to open each valve and effect communication between the reservoir and each of the pressure lines leading from pumps 157, 159, 161 and 163.

The subsystem described immediately above is referred to as the system dump which relieves the pressure lines of each of the pumps so that work need not be done by the compressor engine during the starting thereof. All of the hydraulic fluid in the pumps and immediately adjacent fluid lines will be dumped immediately back into the reservoir so that there is no significant demand on the pump system and little resistance to starting. It is to be understood that the system dump circuitry illustrated in FIG. 8 is part of the basic circuit of FIG. 7 receiving power from the same supply lines 314, 315.

During shut-down and starting of the compacting de vice, ram 121 is fully retracted, tampers 119, are fully raised, and pusher plate 114 is also fully retracted. After the compressor engine has been started, and has reached running speed, switch 318 is shifted to the run position energizing solenoid 320 and opening the normally closed contacts 321-325. This de-energizes the solenoids 326-330 to close relief valves 187, 222, 223, 254 and 310 to permit the flow of hydraulic fluid to the various control valves. With the system in this condition, and the hand-auto switch 323 shifted to the auto position, automatic cycling of the compacting device will begin.

The ram, in its retracted end position, closes limit switch 325, while limit switch 327 remains in its normally closed position. Pressure switch 329 is in its-normally closed position shown in FIG. 7. Normally open contact 331 of relay 320 has been closed by the energization of relay 320. Normally closed contact 333 is closed. With the elements 323-333 in the positionsjust described, relay 335 will be energized by electrical power from the supply lines. Relay 335 actuates contacts 337, 339 and 340, contact 337 closing, contact 339 opening, and contact 340 closing upon energization of the relay 335.

At this time, solenoids 197 and 199 of valves 195 and 196 respectively, and solenoid 231 of valve 229 are energized to cause tampers 119, 120 and pusher 230 to begin forward movement.

At this time, a signal would be supplied to solenoid actuating valve 169 to drive the ram forward, but

for a controlled electrical delay built into the system."

The signal supplied to solenoid 170 upon energization of relay 335 is not received by the solenoid due to the open contact 343 of timer 346. Timer 346, however, is energized by this signal. After a predetermined time lapse, adjustable timer 346 will close contact 343,

effecting energization of solenoid 170 causing forward movement of the ram 121. This adjustable timed delay in the advance of the ram enables the pusher and tampers to press material into the ram chamber 122 before the ram blocks part of its chamber by moving forward. The timed delay may be any amount from 1 to 5 seconds after the electrical signal is applied to the timer and to the solenoids which initiate movement of the moveable compacting members other than the ram. Preferably this delay will be approximately 2 seconds. In no event, however, in the presently described cycle, will the delay of the ram advance be such that the other moveable compacting members will complete their forward strokes before the ram begins to move forward.

As ram 121 moves forwardly after the controlled period of hesitation, it releases limit switch 325 to the normally open position. Relay 335 will remain energized after opening of limit switch 325 since power is supplied tothe relay across its holding contact 337. With contact 337 closed, solenoids 170, 197, 199 and 231 which control forward movement of the ram, the tampers and the pusher plate, will remain energized even after limit switch 325 opens.

When the ram is fully extended into its forwardmost position,-it will open the normally closed limit switch 327 de-energizing relay 335 to open its contact 337 and allow its contact339 to return to the normally closed position. Opening of contact 337 will de-energize solenoids 17.0, 197, 199 and 231 to halt the forward movement of the ram, the two tampers and the pusher plate respectively. At the same time, the return of contact 339 of relay 335 to the normally closed position effects energization of solenoids 171, 195, 200 and 230 to effect return movement of the same moveable compact-' ing members respectively. As the ram reverses its direction of movement and begins to retract, limit switch 327 will return to its normal closed position but relay 335 will not be re-energized until the ram reaches its fully retracted position so as to close limit switch 325. As limit switch 325 is closed, a new cycle will be initiated.

Cycling continues until the material in the last stage of compression, which is being compacted against the gate 124 by the ram 21, reaches a sufficient density as to raise the pressure in the hydraulic supply line to the ram cylinder 175 beyond a predetermined maximum. This predetermined maximum hydraulic pressure, will effect actuation of pressure switch 329 which is connected with the hydraulic line supplying pressurized fluid to the ram cylinder 175. Actuation of pressure switch 329 de-energizes relay 335 to halt the forward movement of the ram, the tampers and the pusher, as described above, while simultaneously energizing relays 341 and 342.

Energization of relay 341 closes contact 343 thereof to hold both relays 341 and 342 energized after pressure switch 329 has returned to the normal position shown in FIG. 7. Relay 342 closes its normally open contact 344 and opens its normally closed contact 345. The closing of contact 344 effects energization of solenoid 262 to shift valve 260 to supply pressurized fluid for opening gate 124.

The above described de-energization of relay 335, upon the attainment ofa maximum pressure at the ram, will, in a manner also described above, effect an opening of contact 339 and consequent reversal of the ram, the tampers and the pusher plate. When the ram reaches its retracted end position, it again closes limit switch 325 causing the cycle to continue.

The opening of gate 124 continues until the gate reaches its fully open position, at which point it will open limit switch 347 de-energizing solenoid 262. In the meantime, the continued cycling of the compacting device causes additional material to move therethrough. New material entering the ram chamber will force the more densely compacted material past the now opened gate to the exterior of the compacting device. When the desired length of densely compacted material has moved outwardly past the gate, this block of material will contact limit switch 349 to open the same. Opening limit switch 349 de-energizes relays 341 and 342. The holding contact 343 of relay 341 will be opened, breaking the holding circuit. Contact 344 or relay 342 will return to its normally open position and contact 345 thereof will be closed. Closure of contact 345 energizes timer 351. The timer 351 includes a normally closed contact 353 which is instantaneously opened upon energization of the contact and a normally open contact 355 which is closed after a timed delay. The opening of contact 353 halts forward movement of the ram by de-energizing solenoid 170 of valve 169, and contact 355 effects a delayed energization of solenoid 261, to in turn delay the shifting of valve 260 to supply fluid pressure for closing the gate 124. Halting the ram and delaying the closure of the gate when the densely compressed material strikes the limit switch 349 insures that the densely compressed material at the exterior of the compacting device will not be in motion as the gate closes thereon slicing the same in a guillc tine fashion. The fact that the compressed material is stationary during severance, in turn, insures that the severed side of the block will be straight.

When the gate reaches the fully closed position it will open the normally closed limit switch 357 deenergizing timer 351. Contact 353 of the timer will return to its normally closed position to re-energize solenoid 170 thereby restoring the supply of pressurized fluid for driving the ram forwardly. The opening of limit switch 357 also de-energizes solenoid 261 so as to cause valve 60 to shift to the center position locking hydraulic fluid in both sides of cylinder 261 to secure the gate in a closed position. It is to be understood that both limit switches 347 and 357 which are opened by the gate at either end of its stroke, prevent deadheading of the cylinder 126 at these end positions thereby eliminating the possibility of excessive pressure buildup in the hydraulic system of the gate.

Depending on the specific condition of operation, it is possible that the travel of the ram 121 may be slower than that of the tampers 119, or pusher plate 114. To prevent dead-heading of the latter and accompanying excessive pressure buildups and excessive power drains from the other systems, limit switches 359 and 361 are provided. The term dead-heading as used herein refers to a condition wherein a moveable compacting member encounters an unyielding resistance, but where fluid pressure continues to be supplied to the hydraulic power cylinders associated with the stalled member. While the unyielding resistance often results when a member reaches the end of its stroke, the term dead-heading as used herein applies to an unyielding resistance encountered anywhere in the stroke.

Limit switch 359 is opened by the pusher plate when the pusher plate reaches its extended, forwardmost position. If the ram has not yet moved into its forwardmost extended position to open limit switch 327 and de-energize solenoid 231 cutting off the flow of pressurized fluid to the pusher cylinders, then the deenergization of solenoid 231 will be accomplished by the opening oflimit switch 359. The same is true for the return stroke of the pusher. If the ram has not already moved into its fully retracted position de-energization of solenoid 230 will be effected by the opening of limit switch 361 by the pusher plate as it moves into its fully retracted position.

Further safety provisions are provided to prevent an excessive buildup on the pusher plate or in its hydraulic circuitry. If a resistance is encountered during the forward stroke of the pusher plate such that pressure in the hydraulic system therefor exceeds a predetermined setting, pressure switch 363 will be triggered energizing relay 365 which opens its normally closed contact 367 and de-energizes solenoid 231. This pressure switch safety feature described immediately above is particularly important when an excessive resistance is encountered by the pusher plate between the end positions of its stroke.

A similar safety feature is also provided for the tampers 119, 120. When either tamper reaches its fully extended position before the ram does, or if either tamper encounters an excessive resistance from material in its compacting chamber 144, a buildup of fluid pressure will occur in the hydraulic system of that tamper. Pressure switch 369 will be triggered by a buildup of pressure in the hydraulic system of tamper 119 to deenergize solenoid 197, shifting valve 195 into the central position and preventing further movement of tamper 119. Likewise, when pressure builds up beyond a predetermined extreme in the hydraulic system of tamper 120, pressure switch 371 will be tripped energizing relay 373 whose normally closed contact 375 will be opened. This will de-energize solenoid 199 as well as solenoid 197 to prevent further forward movement of either tamper. The arrangement is such that when only the tamper 119 furthest from the gate en counters a resistance, the tamper closest to the gate may continue to press material into the ram chamber. However, if tamper 120, which is closest to the gate, encounters resistance, both tampers will stop.

An additional safety feature is found in the provision of contact 331 of relay 320 in the line supplying power to relay 335, the latter controlling the forward strokes of all the moveable compacting members. Unless the switch 318 has been moved to the run position and the relay 320 (which controls the system dump) energized, a signal cannot be produced for initiating forward movement of the compacting members since relay 335 cannot be energized.

Another safety feature is found in the provision of normally closed contact 333 in the same line which supplies power to relay 335. When relay 341 is energized to open the gate 124, contact 333 of that relay will open sending a signal for energizing relay 335 through interlock system 373. This provides an interlock between the operation of the unloader (to be described hereinafter) and the operation of the compacting device 26. If the unloader bucket 298 is not positioned to receive a block of material at the time when the gate opens, the interlock system 373 will block the signal to the relay 335 to prevent advance of the moveable compacting members, to in turn prevent movement of the compacted material outwardly from the ram chamber.

Provision is made for controlling the functions of the compacting device individually, rather than automatically. Moving selector switch 323 to the hand position energizes relay 376 and 377 and cuts off the current supply to relay 335 which controls the automatic cycling of the moveable compacting members. Energization of relay 377 opens its normally closed contacts 379 and 381 to effectively isolate control of the tampers 119, 120 from the other machine functions. With the switch 323 shifted to the hand mode, energization of solenoids 197, 199 to lower the tampers may only be accomplished by manually moving switch 383 to close contact 385 thereof. Likewise, in the hand mode, raising of tampers 119, 120 may only be accomplished by manually moving switch 383 to close contact 387 thereof.

Energization of relay 376 upon shifting switch 323 to the hand position effects the closing of contact 389 of that relay and the opening of contacts 391 and 393 thereof. The opening of the latter two contacts effectively isolates control of the pusher plate from the other machine functions so that solenoid 231, which controls the forward movement thereof, may only be actuated by manually closing contacts 395 of switch 397. Likewise, energization of solenoid 230 to effect return of the pusher plate toward the fully retracted position is accomplished only by manually moving switch 397 to close contacts 399 thereof.

A gate opening switch 400 is also provided for opening the gate 124 independently of the other machine functions. Unlike switches 383 and 397, switch 400 may be used for opening the gate when selector switch 323 is in either the hand or auto position. Manual actuation of the gate'opening system during automatic cycling of the compacting device is useful for clearing the compacting chambers thereof after the last run of the machine. Since the machine will continue to cycle with the gate open, any material remaining in the compacting chambers will be moved through the open gate. Switch 400 accomplishes selective opening of the gate by effecting direct energization of relays 341 and 342 when the switch is moved to the open position the relays then operating in the same manner as described in connection with the automatic cycle.

The circuit of FIG. 7 includes a light 401 disposeed at the operators station and indicating the position of the ram. Another light 402, included in the circuit and also disposed at the operators station, indicates whether relay 320 has been energized, which in turn indicates whether the pumps are supplying pressurized fluid to the hydraulic system.

ADDITIONAL OPERATING CYCLES The automatic cycle and electrical circuitry therefor described above are primarily intended for compacting snow. As part of the present invention, provision is made for readily altering the above described automatic cycle to shift the control apparatus to provide more efficient cycles of operation for handling materials such as solid wastes or ice. Relatively minor changes and additions to the electrical circuitry of FIG. 7 pro vide a solid waste compacting cycle as well as an ice cycle. A three position key switch 403 (FIG. 7a) is provided for selecting the operational mode desired.

in the solid waste compacting mode, gate 124 is not used in a guillotine fashion to cut the blocks of compacted material to length. Instead, a given quantity of solid waste which has been pushed into the compression chamber of the ram by the tampers 119, is compressed against the closed gate 124. When this quantity of material reaches a sufficient degree of compaction as to trigger pressure switch 329, the ram will not reverse its forward stroke as in the snow cycle but, instead, will assume a stationary forward position. The ram remains in this position for a timed delay of up to 5 seconds, during which time the gate 124 remains closed. This delay permits the escape of air from the block of densely compressed solid waste and allows the block to meld. After elapse of the timed interval, gate 124 opens and the ram continues to advance forwardly pushing the block of compacted solid waste to the exte rior of the compacting device 26. The block will actuate a limit switch to initiate return of the ram. When the ram has returned a. sufficient distance, gate 124 is closed and another cycle begins.

Since the ram will be positioned forwardly at the moment when the desired degree of compaction is reached, the ram itself prevents additional material from entering the ram compacting chamber during the timed delay period or during ejection of the compressed block.

In the solid waste compacting mode the moveable compacting members operate sequentially instead of in unison as in the snow cycle. In the solid waste cycle, material entering the charging chamber 139 will be pressed by the pusher plate 114 into tamper chamber 144 while the tampers 119, 120 are poised in their retracted, raised positions. The tampers will not begin their downward stroke until pusher 1 14 reaches its fully extended end position wherein chamber 144 is completely filled with the material. As the tampers begin their downward strokes filling the compacting chamber 122 of the ram 121 with material, the ram remains stationary until the tampers reach their fully extended, lower end positions to entirely fill the compression chamber of ram 21 with material. At this point, the ram begins to move forwardly to complete the final stage of compression as described above.

A third operating mode, referred to as the ice cycle, will be brought into action by turning selector switch 403 to the ice position.

Under certain weather conditions, it is possible for snow entering or contained in the compacting device 26 to turn to ice or to become so heavy as to have characteristics more like ice than snow. For example, the compacting device may be stopped for an interval while snow remains in the chambers thereof. If during this idle interval there is a warm period, possibly with some rain, followed by a colder period, the snow in the machine may turn to ice, and this ice cannot be effectively handled by the ordinary snow compacting cycle. Also, if snow has partially melted or has been mixed with rain, the snow becomes so heavy as to require a cycle other than the usual snow compacting cycle. This is so because the snow compacting cycle is designed to handle large volumes of initially loose material by providing for a continuous flow of material through the compacting device. It has been found, that in order to break up ice which is formed in the compacting device 26 or to effectively handle very heavy snow, a sequential cycle is most effective. Thus, when the compacting device is shifted to the ice mode, the pusher plate 114 will move through its forward stroke first, followed by the forward stroke of the tampers 119, 120 which, in turn, are followed by the forward stroke of the ram. In this respect the ice cycle is the same as the above described solid waste cycle. However, in the case of the ice cycle there is no need for the delay of approximately five seconds after the predetermined pressure on the ram is reached and therefore, this delay is eliminated. Another difference between the solid waste cycle and the ice cycle is that in the ice cycle, the guillotine action of the gate is utilized to cut the block of heavy snow or ice exiting from the ram chamber, to length. The block will trip limit switch 349 in the same manner as in the snow cycle to de-energize relays 341 and 342 to effect closing of the gate.

It is to be understood that while various elements of the electrical circuitry of FIG. 7 have been mentioned with respect to the solid waste and ice handling cycles described immediately above, some of the circuitry associated with these elements will be different from that shown in FIG. 7. FIG. 7 illustrates the circuitry for only one particular compacting cycle.

UNLOADER CONVEYOR The unloader conveyor 28, which is illustrated in FIG. 1 as being attached to the rearward end of the mobile compacting apparatus, will now be described in detail, reference being made to FIGS. 9-12. Referring to FIG. 9, the overall unloader 28 depicted therein may be considered to have two basic sections, namely, a lift section 404 and a transport section 406. The lift section includes a pair of upright beams 408 and 409 which can be best seen in FIGS. 10 and 11. The beams 408, 409 are pivotally connected by means of fasteners4l0, 41 1, respectively to a pair of support arms 414, 415, respectively. Each of the support arms 414, 415 is fixedly secured near the rearward end of one of the frame members 21 of the vehicle chassis 20, each support arm extending vertically upwardly therefrom. A bearing member 418 is disposed between each upright beam and its associated support arm to facilitate pivotal movement of the entire lift section 404 with respect to the vehicle chassis 20.

The transport section 406 includes a pair of elongated, parallel rails 420, 421 having a plurality of rollers 423 extending therebetween for the entire length thereof. An endless conveyor belt 424 passes over the rollers 423 for moving material along the length of the transport section. One end of the transport section 406 is pivotally connected to the upper end of the lift section 404 by a shaft 425. At the other end, namely, the free end of the transport section 406, there is an ear member 428 extending perpendicularly outwardly from the longitudinal axis of each rail 420, 421.

A pair of pulleys 432 are disposed opposite each other and close to the upper rear corner of the lift section 404 near the point where the transport section 406 is pivotally connected thereto. Another pair of pulleys 434 are also disposed laterally opposite each other on the lift section, but at the upper, forward corner thereof. Still another pair of pulleys 435 located on the rearward side of the compacting device 26 are disposed in the same lateral opposing relationship to each other. Directly under the pulleys 435, and also on the rearward wall of the compacting device are a pair of oppositely disposed cable anchors 438. A pair of cables 436 extend in generally parallel fashion from the ears 428. One end of each cable 436 is attached to one of the ears 428 near the outer extremity of that ear, each cable then passing over pulleys 432, 434 and 435 on one side of the unloader. Each cable 436 is then secured at its other end to one of the anchors 438.

A pair of hydraulic cylinders 278, 279, each of which is secured at one end to one of the vehicle frame members 21, are secured at the other ends to a shaft 444. Shaft 444, in turn, is connected at each end to the upright beams 408, 409 near the lower rear corners thereof. A pair of stop rollers 446 are disposed on shaft 444 near the opposite ends thereof. A pair of cage members 448 are connected to the bottom of one of the vehicle frame members 21 and are disposed laterally opposite each other. The cage members have a cross-member 449 extending therebetween. Each cage member 448 includes aleg 450 extending rearwardly at a downward incline.

When hydraulic cylinder 278 is actuated for retraction of its piston rod 282, the lift section 404 of the unloader 28 will pivot about an axis coincident with fasteners 410, 411 in a clockwise direction as viewed in FIG. 9. During this pivotal movement, cables 436 will be placed under tension due to the angular movement of pulley pairs 434 away from stationary pulley pairs 435 and their associated anchors 438. This tensioning of cables 436 creates an upward pull on the ears 428 at points near the outer extremities thereof which, in turn, causes the transport section 406 to pivot about the axis coincident with shaft 425 in a counterclockwise direction as viewed in FIG. 9. The pivotal movements of both the lift section 404 and conveyor section 406 continue until the fully extended position, illustrated by phantom lines in FIG. 9 is reached. In this position, the lift section 404 will be disposed at an angle of approximately 12 with respect to the retracted, vertical position thereof. The transport section, in the fully extended position, will be disposed horizontally with respect to the ground or the vehicle frame and at an oblique angle with respect to the lift section.

When the lift section is in the extended position, stop rollers 446 will engage the inclined legs 450 of the cage members 448 to prevent movement of the lift section 404 beyond the position shown by phantom lines in FIG. 9.

A pair of sliding shoe members 454 engage the forwardmost faces of the upright beam pair 408, 409. The beams 408, 409 act as guides for the shoe members 454 which slide along substantially the length of the beams. The shoes 454 have phenolic or plastic surfaces engaging the surfaces of the beams to reduce sliding friction between the shoes and beams, and to effect smooth and quiet operation. A trunnion shaft 456, secured to the shoe members and extending therebetween, is disposed transversely of the lift section 404. Trunnion shaft 456 will cause the shoe members 454 to move in unison along the beams 408, 409 of the lift section.

The bucket 298, disposed just forwardly of the shoe members 454, has a pair of rearwardly extending arms 458. Arms 458 are disposed laterally opposite each other on either side of the bucket 298. Each arm 458 includes a base portion 460 disposed adjacent to the bucket and a tapered crown portion 462 disposed remotely therefrom. Trunnion shaft 456 pivotably secures the bucket 298 to the shoes.

A pair of lift cables 464 is secured to the shoes and extend upwardly therefrom alongside the lift section 404 and parallel thereto. A lowering cable 466, attached to the trunnion 456, extends downwardly from the trunnion alongside the lift section and parallel thereto. An elongated hydraulic cylinder 280, mounted on the lift section 404, is laterally centered between the upright beams 408, 409 and extends for nearly the entire length of the lift section. Cylinder 280 serves as a motor means for raising and lowering the bucket. An upper sheave 468 is mounted on the lift section above the upper end of the cylinder 280. Cables 469 pass over sheaves 468 and enter through the open ends of cylinder 280 to attach to a moveable piston 470 within cylinder 280. Cables 469 also attach to a moveable frame A lower sheave 472 is journalled on the aforementioned shaft 444 at the lower end of the lift section 404. Cable 466 passes over sheave 472 whereupon it passes over a pulley on moveable frame 473 and then is anchored to the lift section. An analogous arrangement exists for cable 464. A system of pulleys and cables, associated with moveable frame 473 is shown in FIGS. 9 and 10, which system includes cables 464 and 466. The frame, which includes pulleys mounted thereon, is moved by cables 469 which in turn are moved by piston 470. Movement of the frame 473 effects movement of the bucket via cables 464, 466. The pulley system effects a 2 to 1 ratio in bucket movement with respect to piston movement. Thus, as the piston moves a given distance, the bucket will move twice that distance.

Cables 469 are covered with phenolics or plastics and each engage with sealing O-rings at the entry to each end of the cylinder 280. This combination of covered cables and sealing O-rings will retain hydraulic fluid under pressure within the cylinder 280 during movement of the cables through the end openings thereof.

The forwardmost side and uppermost side of bucket 298 are open so as to permit a block of compressed material to enter the bucket as the block is discharged from the ram chamber 122 of the compacting device 26. All other sides of the bucket are closed. The bucket includes bumpers 474 disposed opposite each other near the lower rear corners thereof. When the lift section is in its extended, inclined position, the bumpers 474 engage the shoes 454 to maintain the bucket in the horizontal position as it moves along the lift section 404. The engagement of the bumpers 474 with the shoes also serves to limit the buckets freedom of downward, clockwise (as viewed in FIG. 9) pivotal movement about the trunnion 456.

When the bucket 298 is in its lowermost position on the lift section 404 it will be disposed immediately adjacent the moveable gate 124 of the compacting device 26. Here the bucket is in position to receive compacted material as it is discharged through the open gate. After the bucket has received a compacted block, hydraulic cylinder 280 will be actuated to move the piston 470 upwardly to effect upward movement of the bucket along the length of the lift section.

A pair of cam rollers 476 are located opposite each other on the crown portions 462 of the bucket arms 458. As the bucket approaches the upper end of the lift section, the cam rollers will engage camways 478. One camway is disposed on the inner side of each upright beam 408, 409, so that each roller 476 engages a separate camway. Each camway is formed in a block-like body 479, as best seen in FIG. 12. Each body 479 is disposed on its respective beam at a position slightly below the level of the upper sheave 468. The camway 478 of each body tapers convergently in a direction away from the entry opening 480 thereof.

The camways 478 serve as a gentle stop means for the cam rollers 476 when each cam roller enters its associated camway 478. The rearward curvature and converging taper of the camway 478 will permit the roilers to move only a limited distance therethrough. This will rapidly stop the rollers 476 without causing dangerous impacts.

The rapid halting of the rollers 476 at the end of arms 458, in conjunction with the continued upward movement of the shoes 454 after the rollers are stopped, effects rapid pivotal movement of the arms 458 about the rollers. This rapid pivoting of the arms 458 effects a whip-like movement of the bucket 298 through an arc of approximately into the tilted position shown by phantom lines in FIG. 9. The whipping of the bucket ejects the block of compacted material from the uppermost open side of the bucket so as to direct the block onto the horizontally extending transport conveyor 406. The transport conveyor includes a hydraulic, rotary motor 482 mounted thereon. This motor supplies power to drive the endless conveyor belt 424 about the rollers 423 to move blocks of material along the length of the transport section.

The transport section 406, in its unfolded, horizontal position, will extend above, and rearwardly beyond, the cab of a conventional truck which follows behind the 

1. A compacting apparatus comprising: a. a housing; b. a charging chamber in said housing, said charging chamber being adapted to receive a quantity of material therein, said charging chamber having first and second ends; c. a pusher means for pushing material received in the charging chamber from said first end to said second end and into a confined area; said pusher means having a forward surface facing said confined area and an upper edge adjoining said forward surface; d. a power means for moving said pusher means between said first and second ends of said charging chamber; e. a movable plate having upper and lower sides and being curved along substantially its entire length, said plate being pivotally coupled to said pusher means in the region of said upper edge thereof; f. a straight elongated member disposed in said housing above said pusher means and adjacent said first end of said charging chamber, said elongated member being transversely arranged with respect to the direction of movement of said pusher means, the longitudional axis of said member being fixed with respect to said housing; g. said lower siDe of said curved closure plate engaging said elongated member at all positions of said pusher means, said closure plate being supported from below by said member and movable with respect to said member; h. whereby said closure plate prevents material from being deposited behind said pusher means and is capable of accommodating build-up of relatively heavy material thereabove, thereby facilitating substantially continuous reception of material.
 2. The invention of claim 1 wherein said elongated member comprises a roller rotatable about said longitudinal axis.
 3. The invention of claim 1 including a second member having a longitudinal axis fixed with respect to said housing, said second member being disposed in parallel, closely spaced relationship with said elongated member, a thin, elongated space being defined between said members, said upper side of said curved plate engaging said second member and being movable with respect thereto, the curvature of said closure plate being such that said closure plate moves easily through said space between said members as said pusher means moves between said first and second ends of said charging chamber.
 4. The invention of claim 3 wherein said second member comprises a blade means for removing material from said curved plate during movement thereof, said blade means being pivotable about the longitudinal axis of said second member.
 5. A compacting apparatus comprising: a. a housing; b. a charging chamber in said housing, said charging chamber being adapted to receive a quantity of material therein, said charging chamber having first and second ends; c. a pusher means for pushing material received in the charging chamber from said first end to said second end and into a confined area; d. power means for moving said pusher means between said first and second ends of said charging chamber; e. a movable plate having upper and lower sides and being curved along substantially its entire length, said plate being pivotally coupled with said pusher means; f. a first, straight, elongated member disposed in said housing above said pusher means and adjacent said first end of said charging chamber, said first member being transversely arranged with respect to the direction of movement of said pusher means, the longitudional axis of said first member being fixed with respect to said housing; g. a second, straight, elongated member having a longitudinal axis fixed with respect to said housing, said second member being disposed in parallel, closely spaced relationship with said first elongated member, a thin, elongated space being defined between said first and second members, said curved plate being disposed between said first and second members and being movable with with respect thereto, the curvature of said closure plate being such that said closure plate moves easily through said space between said members as said pusher means moves between said first and second ends of said charging chamber.
 6. The invention of claim 5 wherein said first member comprises a roller rotatable about the longitudinal axis of said first member.
 7. The invention of claim 6 wherein said second member comprises a blade means for removing material from said curved plate during movement thereof, said blade means being pivotable about the longitudinal axis of said second member. 